Classifications

• • A—HUMAN NECESSITIES
  • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
  • A61M—DEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
  • A61M5/00—Devices for bringing media into the body in a subcutaneous, intra-vascular or intramuscular way; Accessories therefor, e.g. filling or cleaning devices, arm-rests
  • A61M5/14—Infusion devices, e.g. infusing by gravity; Blood infusion; Accessories therefor
  • A61M5/142—Pressure infusion, e.g. using pumps
  • A61M5/14244—Pressure infusion, e.g. using pumps adapted to be carried by the patient, e.g. portable on the body
  • A61M5/14276—Pressure infusion, e.g. using pumps adapted to be carried by the patient, e.g. portable on the body specially adapted for implantation
• • A—HUMAN NECESSITIES
  • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
  • A61M—DEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
  • A61M5/00—Devices for bringing media into the body in a subcutaneous, intra-vascular or intramuscular way; Accessories therefor, e.g. filling or cleaning devices, arm-rests
  • A61M5/14—Infusion devices, e.g. infusing by gravity; Blood infusion; Accessories therefor
  • A61M5/142—Pressure infusion, e.g. using pumps
  • A61M5/14212—Pumping with an aspiration and an expulsion action
  • A61M5/14216—Reciprocating piston type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
  • F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
  • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
  • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
  • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
  • F04B19/04—Pumps for special use
  • F04B19/06—Pumps for delivery of both liquid and elastic fluids at the same time
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
  • F04B49/24—Bypassing
  • F04B49/243—Bypassing by keeping open the inlet valve
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/10—Valves; Arrangement of valves
  • F04B53/102—Disc valves
  • F04B53/1032—Spring-actuated disc valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B2205/00—Fluid parameters
  • F04B2205/06—Pressure in a (hydraulic) circuit
  • F04B2205/063—Pressure in a (hydraulic) circuit in a reservoir linked to the pump outlet
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B2205/00—Fluid parameters
  • F04B2205/50—Presence of foreign matter in the fluid
  • F04B2205/503—Presence of foreign matter in the fluid of gas in a liquid flow, e.g. gas bubbles
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
  • F05C2201/00—Metals
  • F05C2201/04—Heavy metals
  • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
  • F05C2201/0448—Steel
  • F05C2201/046—Stainless steel or inox, e.g. 18-8

Definitions

• This invention relates to the art of electro- magnetically operated fluid pumps, and more particularly to a new and improved electromagnetic pump which operates at extremely low power.
• the principal requirements for a pump for use in implantable drug delivery systems are low power drain, since the pump must be driven by an implanted battery, and compatibility with the drug being pumped. Another important requirement is that the pump be capable of operating with bubbles present in the liquid being pumped.
• a related consideration is that the bubble pumping capability provided in the pump not give rise to inaccuracy caused by inertia of the fluid stream. Such inertial effect is a result of the momentum of the fluid stream being capable of maintaining motion of the stream for some time after completion of the pump piston stroke, and the fluid volume delivered as a result of the stroke is thereby increased.
• a further pump design consideration is providing a relatively small displacement pump which pumps bubbles in a manner equivalent to that of a larger displacement pump.
• the objects of this invention are to provide an electromagnetically operated pump which is safe, reliable, small in size, light in weight, which operates without excessive demand on the available energy supply, which is compatible with drugs or similar liquids to be pumped, which is capable of operating with bubbles present in the liquid being pumped, wherein the inertial effect on pump accuracy is reduced, and wherein the bubble pumping capability is not reduced by a reduction in pump displacement.
• the present ' invention provides an electromagnetic pump comprising a housing having a fluid receiving chamber in communication with an inlet, a fluid pumping chamber in fluid communication with an outlet, check valve means operatively associated with the fluid receiving chamber for allowing fluid flow in a direction from the inlet toward the outlet and blocking fluid flow in a direction from the outlet to the inlet, electromagnet means carried by the housing located external to the fluid chambers thereof, and barrier means in the form of a thin diaphragm of fluid impermeable material which hermetically isolates the electromagnet from the fluid chambers.
• An armature movable in the housing has a pole portion located for magnetic attraction by the electromagnet means and has a piston portion to force fluid out of the chambers and through the pump outlet.
• the armature piston portion is movably supported in the pump housing and located on the inlet side of an armature plunger.
• the armature is moved from a rest position through a forward pumping stroke when attracted by the electromagnet means to force fluid from the receiving chamber through the outlet, and the armature is moved by biasing means in an opposite direction through a return stroke back to the rest position.
• controlled means for providing a bypass path for bubbles and fluid around the armature piston portion between the fluid pumping chamber and the fluid receiving chamber only during the return stroke of the armature.
• the fluid inertial effect is reduced by means for providing an orifice in the path of fluid flow from the pump outlet and by means in the bypass path for providing an orifice for fluid flow in that path, the outlet and bypass orifices being provided either individually or in combination depending upon the fluid flow characteristics of the system of which the pump is a part.
• An accumulator means in the fluid flow path between the pump outlet and a catheter leading away from the pump alleviates inertial and viscous effects arising from the catheter.
• the armature pole portion has a fluid-contacting section of material which is compatible with and corrosion resistant to the fluid, and in one aspect is a body of magnetic material within a titanium enclosure and in another aspect is a body of chrome- molybdenum-iron alloy.
• the check valve means and inlet are so arranged that the pump displacement can be reduced without reducing the bubble pumping capability of the pump.
• FIG. 1 is a longitudinal sectional view of a pump according to one embodiment of the present invention
• Fig. 2 is longitudinal sectional view, partly in eluation, of a pump according to another embodiment of the present invention.
• Fig. 3 is an enlarged view taken within the region in Fig. 2 outlined by dotted lines;
• Fig. 4 is a fragmentary side elevational view, partly diagrammatic, illustrating a pump arrangement according to another embodiment of the present invention.
• Fig. 5 is a fragmentary longitudinal sectional view of a pump according to another embodiment of the present invention
• Fig. 6 is a fragmentary longitudinal sectional view of an alternative version of the pump of Fig. 5.
• a pump 10 includes a housing 12 which is generally hollow, either rectangular or cylindrical in overall shape, and pump 10 includes an interior region for containing fluid, i.e. the liquid to be pumped.
• the hollow interior region is divided in a manner which will be described into a fluid receiving chamber 14 and a fluid pumping chamber 16 in fluid communication therewith.
• inlet port 18 is adapted to be connected to a source or supply of fluid to be pumped
• outlet port 20 is adapted to be in fluid communication with a location to which fluid is to be pumped.
• check valve means generally designated 24 operatively associated with the fluid-containing region of pump 10 for allowing fluid flow in a direction from the inlet 18 through outlet 20 and blocking fluid flow in a direction from the outlet through the inlet.
• check valve means 24 is within the pump and associated with the pump armature in a manner which will be described.
• Housing 12 is generally hollow including a first body portion 30 of relatively substantial wall thickness. Housing 12 also includes a first axial end portion 32 extending from one end of body 30, i.e. the right-hand end as viewed in Fig. 1, and which is of relatively smaller wall thickness terminating in an axial end face 34. Housing portion 30 defines an interior region of constant diameter having an inner surface 36. The housing portion 30 terminates at the other end thereof, i.e. the left-hand end as viewed in Fig. 1, in an end face 38. Housing 12 includes a second or central body portion 40 which defines an interior region of constant diameter having an inner surface 42. Body portion 40 has' a first axial end face portion 44 which contacts the end face 38 of body portion 30.
• An annular flange or rim 46 extends axially beyond end face portion 44 and is received in an annular shoulder defined between end face 38 and the outer surface of body portion 30.
• the outer surfaces of body portions 30 and 40 are of substantially equal cross-sectional shapes and dimensions so as to be substantially flush.
• Housing 12 further comprises a spring retainer element 50 in the form generally of a bushing having an outer dimension substantially equal to the outer dimension of body portion 40 so as to be substantially flush therewith.
• Element 50 includes an axial extension 52 having an outer diameter substantially equal to the inner diameter of the body portion 40 so as to be received therein in a tight friction-like fit.
• Extension 52 terminates in an annular shoulder defined by axial and cylindrical surfaces 54 and 56, respectively, for providing a spring retaining function in a manner which will be described.
• the opposite end of element 50 terminates in an axial end face 60.
• An annular shoulder is defined by cylindrical and axial surfaces 62 and 64, respectively, at the peripheral junction between end face 60 and the outer surface of body 40.
• the shoulder receives one end of a first weld ring element 70 having an outer diameter substantially equal to the outer dimension of element 50 so as to be substantially flush therewith.
• Ring element 70 is welded at the one end thereof, i.e. the right-hand end as viewed in Fig. l, to element 50 at the aforementioned shoulder thereof in a suitable manner.
• Ring 70 is joined at the opposite end thereof to other components of the pump housing in a manner which will be described.
• Pumping chamber 16 is placed in fluid communication with outlet port 20 in the following manner.
• An axially extending opening or passage 80 is provided in the body of retainer element 50, extending axially inwardly from end face 60, and a longitudinal bore or passage 82 is provided in housing body portion 40 and terminates in a generally cylindrical chamber in registry with port 20 at the other end thereof.
• Housing portion 40 is provided with a radially extending bore or passage 84 into which is fitted one end of a conduit or fitting 86 which comprises a portion of the afore ⁇ mentioned fluid circuit and which will be described in further detail presently.
• pumping chamber 16 is placed in fluid communication with outlet port 20 via the arrangement of passages 80, 82 and 84.
• Chamber 16 is placed in fluid communication with fluid receiving chamber 14 in the following manner.
• Another axially extending opening or passage 90 is provided in the body of retainer element 50, extending axially inwardly from end face 60 and located substantially diametrically opposite the passage 80.
• Body portion 40 is provided with a longitudinally extending bore or passage 92 located so as to be in fluid communication with passage 90.
• a radially extending opening 94 in body 40 meets passage 92 at the end thereof.
• Inlet port 18 is provided by the following arrangement.
• a cylindrical recess of short axial length is provided in housing axial end face 34 and terminates in an inner annular end face 100.
• the inner surface 102 of the recess has a diameter larger than that of housing inner surface 36.
• Surfaces 100 and 102 define an annular shoulder which receives the cylindrical body of a ferrule element 104 in a tight-fitting relationship.
• Ferrule 104 has an inner axial end face 106 provided with a central, boss-like axial extension 108 having an axial end face provided with an annular valve formation 110 which is shaped to define a sharp annular edge facing axially into the housing interior region.
• a central bore or passage 112 of constant diameter extends axially inwardly from valve formation 110 whereupon it meets a passage 114 of increasing diameter.
• Ferrule 104 also has an outer axial end face 116 which extends axially outwardly from housing end face 34 for a short distance.
• a cylindrical recess 118 is formed in end face 116 and extends inwardly for about half the axial length of ferrule 104.
• a cap 120 having a cylindrical outer shape is received in recess 118.
• Cap 120 has a central opening 122 into which is fitted one end of a conduit or fitting 124 which comprises a portion of the fore-mentioned fluid circuit and which will be described in further detail presently.
• Opening 122 has an end portion 126 of increasing diameter substantially corresponding to passage 114 of ferrule 104.
• a flow path is defined through the central passage of cap 120 and the passage portions 112 and 114 thereby defining inlet port 18.
• a disc-shaped filter element 128, preferably of the etched titanium type, is fitted between ferrule element 104 and cap 120 as shown in Fig. 1 so as to be in the flow path.
• the pump of the present invention further comprises electromagnet means generally designated 130 carried by housing 12 and located external to the fluid containing region of the housing. As shown in Fig. 1 the electromagnet 130 includes a core 132 in the form of a spool which is generally solid cylindrical in shape.
• a coil 134 is wound on spool 132 and contained within a hollow housing 136 generally cylindrical in shape.
• a sleeve-like body 138 of encapsulant material is between coil 134 and housing 136 and extends axially inwardly around the end of coil 136 facing housing 12.
• One end of electromagnet 130 is adjacent and in abutting relation to housing 12 and the opposite end, i.e. the left-hand end as viewed in Fig. 1, is closed by an arrangement including a washer 140 and a body 142 of encapsulant such as epoxy material.
• a pair of terminals one of which is designated 144 provide electrical connection from a power source, such as a lithium battery charging circuit and capacitor, to electromagnet 130 via a pair of conductors, one of which is designated 146. Electromagnet 130 is joined to housing 12 in the following manner.
• the interior, fluid containing region of housing 12 and the electromagnet 130 are separated by a barrier means of fluid impervious material in the form of a relatively thin plate or diaphragm-like component 160.
• a second weld ring 162 is provided on the end of magnet housing 136 adjacent housing 12. The outer diameter of ring 162 is substantially equal to the outer diameter of the first weld ring 70 so that the respective outer surfaces are substantially flush.
• the region between coil 134 and barrier 160 is occupied by the annular ring portion of encapsulant 138.
• the housing and electromagnet structures are placed in abutting relation on opposite sides of the plate 160, and the assembly is secured together by a weld joining the respective outer surfaces of the weld rings 70 and 162.
• an enlarged annular end portion 168 of spool 132 contacts the central portion of plate 160 in a manner supporting the same.
• the pump according to the present invention further comprises an armature generally designated 200 positioned in the fluid containing region of housing 12.
• the armature has a pole portion 202 located for magnetic attraction by the electromagnet 130.
• the armature has a piston portion 204 associated with the fluid receiving chamber 14 for moving fluid from chamber 14 into chamber 18.
• the armature has the pole portion 202 for movement within chamber 18 as shown in Fig. 1.
• the armature 200 is movably supported in housing 12 for movement from a rest position through a forward pumping stroke when attracted by the electromagnet 130 to force fluid out of the chambers 14 and 16 through outlet 18, and for movement in an opposite direction through a return stroke back to the rest position.
• armature 200 is shown in the rest position at the end of the return stroke.
• Armature 200 includes a shaft or rod portion
• Armature 200 includes a pole portion generally designated 202 which occupies a major portion of chamber 16 in which it is located, and pole portion 202 has a lateral dimension as viewed in Fig. 1 which is several times greater than the longitudinal dimension thereof.
• pole portion 202 comprises a body of magnetic material within a titanium enclosure, the encapsulation provided by the titanium enclosure providing protection against corrosion from insulin stabilized for use in implantable delivery systems and other corrosive drugs.
• pole portion 202 comprises a body 206 in the form of a disc.
• the enclosure comprises a thin-walled cap 208 having a base 210 contacting one axial face of disc 206 and an annular rim 212 contacting the periphery of disc 206.
• the enclosure is completed by a disc ⁇ shaped body 214 contacting the opposite axial end face of disc 206 and abutting the rim 212 of cap 208.
• rim 212 of cap 208 extends slightly axially beyond the periphery of disc 206, body 214 fits within and contacts rim 212, and a weld ring 220 embraces the periphery of rim 212 so that ring 220, rim 212 and the disc-shaped body 214 can be welded together at the junctions thereof.
• the disc-shaped body 214 is provided with at least one vent passage 224 therein to evacuate residual gas during assembly, the passage 224 being sealed by a plug 226 after assembly.
• Passage 224 is in the form of an axially extending through bore in body 214.
• the provisions of passage 224 and plug 226 is necessary because the small residual volume of gas within cup 208 must be evacuated to hold cup 208 tight against disc 206 even when the interior of pump 10 is at low pressure.
• Plug 226 is in the form of a filler pin and is welded in place with the entire assembly under vacuum to close the vent hole 224 in body 214.
• the armature pole portion 202 terminates at the end facing electromagnet 130 in an axial end face which serves as the pole face and is disposed substantially perpendicular to the armature axis.
• the armature pole face together with electromagnet 130 define the magnetic circuit gap which is closed during the forward armature stroke.
• the pole face is of relatively large cross-sectional area as compared to the cross sectional area of the armature piston portion 204.
• the armature pole portion 202 serves as the plunger portion of the armature, and as the pole face moves toward plate 160 when magnet 130 is energized, pole portion 204 upon moving in chamber 16 displaces fluid and moves it toward outlet 20.
• Armature shaft portion 205 is joined to the pole portion 202 via a sleeve-like axial projection or bushing 232 extending from disc-shaped body 206 to which is attached an armature rod or shaft 234.
• the outer diameter of bushing 232 is slightly smaller than the inner diameter of retainer element 50 so that bushing 232 is freely longitudinally movable along within retainer 50. The attachment is made by crimping the bushing 232 which allows the overall length of the piston assembly to be changed to adjust the piston stroke.
• Shaft 234 is provided with an enlargement at the end opposite bushing 232 which includes two relatively larger diameter shaft sections. In particular, there is a first section 236 facing bushing 232 and a second, axially adjacent section 238 which is larger diameter.
• the section 236 is of relatively shorter axial length, and the sections 236, 238 define therebetween a shoulder facing pole portion 204.
• biasing means in the form of a coil spring 244 for urging armature 200 toward the rest position shown in Fig. 1.
• One end of spring 244 seats in the annular shoulder defined by the armature shaft sections 236, 238.
• the opposite end of spring 244 seats in the annular shoulder defined by surfaces 54, 56 of retainer element 50 previously described.
• Retainer 50 is concentric with the armature shaft portion 202 and receives spring 244 which also is concentric with armature shaft portion 202.
• the armature shaft portion 202, in particular bushing 232 is freely axially movable within retainer 40.
• Armature 200 includes a piston portion generally designated 250 movably positioned within the interior region of housing portion 30 and extending axially from armature body portion 238 toward inlet 18.
• Piston 250 is substantially cylindrical in shape having a first section 252 axially adjacent body portion 238 of relatively smaller diameter for a purpose to be described and a second section 254 of diameter slightly larger than section 252.
• Section 254 also is of greater axial length as compared to section 252.
• the outer diameter of section 254 is slightly less than the diameter of the interior passage in housing portion 30 to allow reciprocal movement of piston 250 within housing portion 30 during the forward and return strokes of armature 200.
• Section 254 terminates in an axial end face 256 which faces toward inlet 18.
• the pump includes check valve means 24 operatively coupled to the armature 200 and located in the fluid-receiving region of the housing for operating and closing the pump inlet.
• the check valve means 24 comprises a valve member positioned and biased for closing the pump inlet when the armature is in the rest position and allowing opening of the inlet after the armature begins movement associated with the forward pumping stroke.
• check valve means 24 is located in the fluid-receiving chamber 14 between inlet 18 and the armature piston end face 256.
• Check valve means 24 includes a body or seat 260 in the form of a disc having a surface facing and adapted to sealingly contact the edge of the valve formation 110, a backing element or plate 262 contacting disc 260, a shim 264 contacting armature end face 256, and a biasing spring 266 in the form of a conical spring between backing element 262 and shim 264.
• the valve seat 260 is loosely positioned in the passage and is relatively thin. As a result, seat swelling caused by temperature changes or the presence of various liquids has a smaller effect on the liquid volume delivered per stroke. This seat structure makes it possible to reduce the clearance between seat 260 and the passage in housing portion 30.
• the small clearance and thinner seat 260 together contribute significantly to reducing the volume of the fluid-receiving chamber 14 with armature 200 in the rest position.
• the backing element 262 provides a bearing surface for spring 266 at all times and when armature 200 is at rest.
• the biasing spring is compressed to an approximately flat configuration as shown in Fig. l when armature 200 is in the rest position.
• the arrangement and structure of check valve means 24 and the provision of conical spring 266 minimizes the internal volume of the pump thereby limiting the maximum size of a bubble which can be contained therein.
• the pump of the present invention further comprises a bypass passage in the pump body between the pumping chamber 16 and the fluid receiving chamber 14 to provide a path for bubbles and fluid around the armature piston, which is closely movably fitted within the pump body, and check valve means in the bypass passage which opens during the return stroke of the armature 200.
• the need for the bypass path arises from the small clearance between piston section 254 and the passage in housing portion 30 requiring a potentially high pressure difference to force bubbles therethrough and the possibility of a bubble becoming trapped between piston section 254 and the passage and preventing return of armature 200.
• housing portion 30 is provided with a longitudinally extending bore or passage 270 radially offset from the central interior passage and extending axially inwardly from an end face 272 a distance beyond the center of body 30.
• a radially extending bore or passage 274 places passage 270 in communication with the central interior passage substantially mid-way between the axial ends of housing portion 30.
• passage 274 is of relatively small diameter to function as a bypass orifice means to decelerate the flow rapidly at the end of the pump stroke to thereby reduce the inertial flow volume in a manner which will be described.
• annular valve seat surface 276 formed in body 30.
• a check valve generally designated 280 normally blocks communication between passages 270 and 274.
• Check valve 280 includes a disc-shaped body or seat 282 having one surface contacting the annular valve seat surface 276 and a conical biasing spring 284 between valve body 282 and a plug 286 fitted in body 30.
• the bypass check valve 280 provides a different path for bubbles past the armature piston portion 250. It is designated to open at a pressure head well below the pressure generated by the armature return spring 244. Preferably, the opening pressure for check valve 280 is also lower than the bubble point of the gap between piston section 254 and the passage.
• the provision of bypass check valve 280 causes a rapid return stroke of armature 200, since the armature return no longer is limited by the rate of fluid leakage between armature piston 250 and the passage. Instead the major part of the fluid moves from pumping chamber 16 along passage 270 through check valve 200 and passage 274 into chamber 14 along with any bubbles contained in the fluid.
• bypass check valve 280 as an alternate bubble path offers two principal advantages. First, it reduces the dependence of the pump behavior with bubbles present upon the fluid surface tension, the surface properties of armature piston 250 and the interior passage of housing portion 30, and the clearance between piston 250 and the passage. Second, and perhaps more important, it preserves the continuity of the liquid film between piston 250 and the passage of body 30 during bubble passage, which liquid film plays an important role in operation of the pump.
• the outlet conduit or fitting 86 which extends from outlet 20 provides a path for fluid flow from pump 10 and comprises a relatively rigid tubing.
• One end of tubing 86 is connected to pump outlet 20 and the orifice providing means 290 is located adjacent the other end of tubing 86.
• a length of relatively rigid outlet tubing 292 is provided with one end 294 tightly fitted on or otherwise properly secured to the end of fitting 86.
• Tubing 292 can be of any required length and the other end is located at a point of use for the fluid being pumped.
• inner section 298 having a diameter substantially equal to the outer diameter of fitting 286.
• Section 298 extends axially inwardly a relatively short distance where it meets a radially inwardly extending wall portion 300 which is provided with a small diameter central bore or passage 302 providing the afore-mentioned orifice.
• Wall portion 300 includes inwardly tapering surfaces so that passage 302 is of relatively short axial length.
• the remainder of the axial length of tubing 292 has a constant diameter inner section 304 which in the present illustration is of smaller diameter than section 298.
• inlet 18 is connected to a source or supply of fluid to be pumped, and outlet 20 is connected via tubing 292 to a point or location of use for the pumped fluid.
• the armature 200 is moved through a forward pumping stroke in response to electrical energization of electromagnet 130.
• One way of energizing magnet 130 is to charge a capacitor from a battery and then discharge that capacitor through coil 134.
• Other procedures can of course be employed for electrically energizing coil 134 in a known manner.
• armature 200 Prior to electrical energization of magnet 130, armature 200 is in the rest position illustrated in Fig.
• Electromagnetic flux travels through the magnetic circuit including the electromagnet core 132, washer 140, magnet housing 136, the included portion of the periphery of diaphragm 160 between the end face of housing 136 and cap 208, armature pole body 206, and the gap between the armature pole face and diaphragm 160.
• the check valve 24 moves freely with respect to the armature 200 and does not necessarily move when the armature 200 is drawn toward diaphragm 160.
• the surface of check valve body 260 is held in contact with the edge of the valve formation 110 by the spring 244 acting upon the armature 200 which is then in contact with check valve body 260 and the compressed spring 266.
• the force of spring 244 is no longer transferred to the check valve 24 and the force holding the surface of check valve body 260 against the valve formation 110 is decreased to that provided by spring 266, which generally provides a force less than that provided by spring 244.
• the forward pumping stroke of the armature 200 is completed when the armature pole face approaches contact with the diaphragm 160.
• the armature velocity decreases to a level such that the displacement rate of the motion of the pole portion 202 no longer exceeds the leak rate between the outer surface of armature piston section 250 and the central interior passage of housing portion 30, the pressure within the pump housing 12 begins to increase.
• the check valve member 260 moves toward the valve formation 110 and prevents flow out of the inlet port 18 of the pump.
• armature 200 When electrical excitation of coil 134 ceases, armature 200 is moved in the opposite direction, i.e. to the right as viewed in Fig. 1, by the force of biasing spring 244 until the armature reaches the rest position as shown in Fig. 1.
• the bypass check valve 280 is open with the result that the return motion of armature 200 is relatively rapid as previously described.
• check valve 24 is held against valve formation 110 primarily by the force of spring 266 supplemented by the difference between the outlet and inlet pressures acting on the check valve seat.
• the return stroke is completed the spring force is increased to that of spring 244.
• the average pumping rate is determined by the rate of return of armature 200 to the rest position.
• the surface of barrier 160 facing armature 200 is provided with a slightly conical shape with the apex or tip 310 of the cone pointing toward or facing armature 200.
• the cone thus defined is very blunt and nearly flat, the angle of the cone measured relative to the longitudinal axis of pump 10 being approximately 89°.
• the taper of this conical surface of barrier 160 is sufficient to change the behavior of the armature 200 during the return stroke thereof as compared to a completely flat or planar surface of barrier 160.
• the conical surface of barrier 160 is believed to reduce the pressure difference at the armature pole face which may occur if a gas-liquid interface should encircle the armature pole face surface in contact with barrier plate 160.
• the conical surface of barrier 160 serves to reduce the force which may under certain circumstances hold the armature pole face close to the barrier 160 in the presence of a liquid-gas interface.
• the conical surface of barrier 160 also serves to decrease the time required for the armature pole face to separate from the barrier 160 at the beginning of the plunger return stroke. This is a viscous flow effect and occurs even if no liquid gas interface is present.
• the relatively smaller diameter of armature piston 250 as compared to pole portion 202 allows it to pump against higher back pressures without saturating the existing magnetic circuit.
• An additional advantage of this configuration is that for a given stroke volume, the smaller diameter of piston 250 allows that the linear stroke be longer. This tends to improve the stability of the stroke volume since the effect of seat swelling or stroke volume is smaller.
• Another advantage arises from the fact that the volume of the pump chamber 14 with armature 200 in the rest position is smaller for the smaller combination of piston 250 and the passage in housing portion 30.
• the smaller diameter section 252 of piston 250 provides a necking down of the piston at its downstream end for the purpose of reducing the tendency of a bubble to be drawn back into the clearance between armature piston 250 and the passage in housing portion 30.
• the film maintains the required pressure drop on opposite sides of piston 250 during the pumping stroke, and a gas bubble in that clearance could provide a leak thereby tending to equalize pressure on opposite sides of piston 250.
• the necked down section 252 of piston 250 provides a route by which liquid may move around a bubble in the space between section 252 and the passage in housing portion 30 and thereby move into and along the gap between piston section 254 and the passage in housing portion 30.
• the pump 10 according to the present invention thus has the capability of operating with bubbles in the inlet stream.
• bypass orifice location has the advantage that the orifice 274 does not affect the flow during the pump stroke.
• bypass check valve 280 is closed during the forward pump stroke and there is no flow through the bypass orifice 274 until the pump stroke is complete.
• the flow now driven by the momentum of the fluid stream, is diverted primarily through the bypass orifice 274.
• a small part of the flow passes through the small clearance between the armature piston 250 and housing portion 30.
• the pressure drop of the flow through the orifice 274 then combines with the pressure drop through the remainder of the system to decelerate the flow and limit the inertial flow volume.
• the downstream orifice location has the effect that the main flow must pass through orifice 302 during the actual pump stroke. There is therefore a substantial pressure drop in the flow during the actual pump stroke which may extend the time duration of the actual pump stroke and increase required energy of the driving electrical impulse. As a result of the extended stroke time and the possibly increased pressure difference across the armature piston 250, the flow leakage around the piston 250 may increase thereby tending to decrease pump accuracy.
• the downstream orifice 302 of proper size can increase the accuracy of a pump tubing combination without imposing a significant performance penalty.
• downstream orifice 302 is particularly effective in controlling the inertial effect associated with rigid or non-compliant tubing in the flow path from the outlet of pump 10.
• the downstream orifice 302 ensures that fluid pressures within pump 10 remain positive during deceleration, and orifice 302 provides a mechanism for decreasing the fluid stream rapidly thereby reducing its momentum.
• orifice 302 installed at the downstream end of any hard, i.e. non- compliant, tubing which must be attached directly to pump outlet 20 offers an effective solution to the problem of flow inaccuracy due to inertial effects.
• an illustrative pump having a normal pulse volume in the range from about 0.4 ⁇ L to about 0.6 ⁇ L, providing orifice 302 with a diameter of about 0.005 inch has been found to provide satisfactory results.
• the magnetic material for body 206 can be chosen without concern for corrosion resistance.
• a 4750 nickel-iron alloy for body 206 has been found to provide satisfactory results.
• Pump 10 accordingly has the advantages of operating at extremely low power levels, being compatible with drugs and similar liquids to be pumped, being electrically and magnetically efficient, being small in size, light in weight and reliable in operation, having the capability of operating with bubbles in the input liquid stream, and reducing the fluid inertial effect on pump accuracy.
• the non-movable diagram 160 of titanium or like material provides an hermetic seal between the fluid in housing 12 and the electrical components associated with electromagnet 130. Having armature 200 immersed in the fluid makes operation of the pump nearly independent of ambient pressure.
• the initial condition of the pump 10 when armature 200 is in the rest position of Fig. 1, is that fluid is at substantially the same pressure on opposite sides of the armature pole portion 202, i.e. in the two chambers 14 and 16.
• the pump 10 of the present invention is made electrically and magnetically efficient by minimizing the total gap within the magnetic circuit, by having the magnetic pole face of armature pole portion 202 of relatively large surface area, and by having core 132 of relatively small cross-sectional area.
• diaphragm 160 is relatively thin in relation to the afore-mentioned contact area.
• the relatively small diameter of core 132 provides the necessary number of ampere turns with a minimum electrical resistance.
• the large area of the pole face of the disc-shaped armature pole portion 202 provides a high magnetic force with a minimum number of ampere turns. Having the magnetic gap external to coil 134, i.e. between the armature pole face and diaphragm 160, allows the foregoing features to be achieved simultaneously.
• Figs. 2 and 3 show a pump 330 according to another embodiment of the present invention.
• Components of pump 330 similar to those of pump 10 are identified by the same reference numeral with a prime designation.
• a principal difference between the two embodiments is that armature 332 in pump 330 is simpler in structure and relatively easier to manufacture and assemble.
• armature 332 has a pole portion 334 comprising a solid, monolithic body having the shape or form of a disc.
• the lateral dimension of pole portion 334 is several times the longitudinal dimension thereof.
• Pole portion 334 has a first axial end face 338 which faces toward barrier means 160' and a second, opposite axial end face 340 which faces toward inlet port 18' .
• end faces 338, 340 are disposed substantially perpendicular to the direction of travel of armature 332.
• Pole portion 334 is exclusively of magnetic material, preferably a chrome-molybdenum-iron alloy which is heat treated. Examples are 29-4 and 29-4C chrome-molybdenum iron alloy. This alloy has high corrosion resistance, and has adequate magnetic characteristics for use in pump 330 when heat treated. In other words, the alloy is heat treated to provide a BH characteristic for the alloy which yields the requisite level of magnetic flux density and coercive force. Furthermore, the alloy is sufficiently resistant to corrosive effects of insulin stabilized for use in implantable drug delivery systems as well as other corrosive drugs.
• the afore-mentioned chrome- molybdenum-iron alloy is a ferritic stainless steel alloy containing 29% chromium, 4% molydenum and the remainder substantially iron.
• the afore-mentioned heat treatment involves an anneal and rapid cool of the armature pole portion 334.
• the procedure involves a short magnetic anneal at a temperature above that which can form a harmful second phase in the alloy followed by cooling rapidly enough to avoid second phase formation but not so rapidly as to degrade magnetic properties.
• Heating of armature pole portions 334 of 29-4 alloy is performed for example in a clamshell furnace at a temperature of about 1010°C for about twenty minutes whereupon the parts 334 are removed quickly to the ambient in a manner allowing complete cooling for a minimum of 25 minutes.
• the cooling rate during the first portion of the cooling cycle from 1010°C down to black, i.e. down to 600°C, should be maintained at about 60 seconds.
• the armature body or pole portion 334 is provided with at least one passage means therethrough, and in the pump shown two axially extending through bores or passages 342, 344 are shown.
• the passages 342, 344 extend through the entire axial length of armature body 334 between the axial end faces 338, 340.
• Passage means 343, 344 serve to reduce the time required for armature pole portion 334 to separate from barrier means 160' during movement of armature 332 toward port 18' and to reduce surface tension effects between barrier means 106' and pole portion 334.
• barrier 160' is provided with a central conical formation identical to that of barrier 160 in the embodiment of Fig. 1 and which functions in an identical manner for the same purpose.
• armature shaft portion 350 which simply is fastened at one end to the pole portion 334.
• armature shaft portion 350 comprises a rod-like body 352 having an axial end face 354 which abuts the axial end face 340 of pole portion 334.
• a rivet 356 or similar fastening means is employed to simply attach shaft portion 350 to pole portion 334.
• the outer diameter of rod 352 is slightly smaller than the inner diameter of spring retainer 50' .
• Armature shaft portion 350 meets an annular enlargement 360 which defines with the adjacent portion of shaft 350 an annular shoulder for receiving one end of biasing spring 244' .
• the remainder of the armature comprises piston portion 250' including the first and second sections 252' and 254', respectively, wherein section 252' meets enlargement 360.
• the foregoing armature structure avoids problems involving criticality of alignment during assembly of pump 330.
• Pump 330 illustrates an alternative arrangement for providing an orifice in the fluid bypass path.
• the orifice providing means comprises a plate-like element 364 having a central through bore to define the bypass orifice.
• element 364 is of metal in the shape of a disc and is force-fitted or otherwise suitably secured in a chamber 366 formed at the end of passage 270' .
• Element 364 is located in chamber 366 so as to serve also as a valve seat for by-pass check valve 280' .
• a small diameter bypass orifice 370 is drilled or otherwise provided generally centrally of element 364, and orifice 370 is in fluid communication with a radially extending bore or passage 372 leading from the central passage in housing portion 30'.
• inlet 18' is provided by an arrangement including an inlet fitting 380 in axially abutting relation with the end face of housing portion 30' and having a central boss-like extension 382 which terminates in an annular valve formation 384.
• a sealing ring 386 seated in a recess in the inner end surface of fitting 380 provides a fluid seal between fitting 380 and housing portion 30' .
• a central recess in the outer end face of fitting 380 receives a filter plug element 390 provided with a laterally extending bore or passage 392 in communication with an inlet port opening 394 provided in the wall of fitting 380.
• a relatively short longitudinally extending bore or passage 396 in element 390 places passage 392 and thus inlet port 394 in fluid communication with the central passage in housing portion 30' .
• a disc-shaped filter element 400 preferably of the etched titanium type, is located between fitting 380 and plug 390 and in the fluid flow path.
• Pump 330 operates in a manner similar to pump 10 shown in Fig. 1.
• the catheter used to lead the drug from the pump to the infusion site may be of relatively long length and small diameter and also be of low compliance. With catheters of the smallest probable diameters, the catheter could offer such high resistance to the flow during the pump stroke that the performance of a pump in such a system could be degraded seriously.
• a small accumulator is provided downstream of the pump outlet orifice large enough to contain the pulse volume of the pump with a reasonable pressure rise.
• the catheter diameter may then be small enough to ensure that the flow through the accumulator catheter combination is critically damped and no flow oscillations occur which might otherwise draw additional flow through the pump check valves. It is desirable that the accumulator be small enough so that a significant pressure rise occurs during the pump stroke.
• the back pressure build-up serves the purpose of preventing a large pulse volume when the supply pressure exceeds the delivery pressure.
• component 420 is a pump according to the present invention such as pump 10 of Fig. 1 or pump 330 of Figs. 2 and 3.
• An inlet tube 422 connects the inlet port of pump 420 with a source of fluid (not shown) wherein arrow 424 indicates the direction of fluid flow in the system.
• a pair of electrical leads 426, 428 connects pump 420 to an appropriate power source (not shown) as previously described.
• the arrangement further indicates an outlet tube 430, one end of which is connected to the outlet port of pump 420 and the other end of which is connected to one end of an accumulator 436.
• accumulator 436 is connected to one end of a catheter 440, the other end of which is connected to a liquid infusion site (not shown) .
• outlet tube 430 is relatively rigid and accumulator 436 is in the form of a small compliant element.
• accumulator 436 can comprise a small length of silicone rubber tubing, i.e. about 1/2 inch in length and 1/32 inch inner diameter in an illustrative arrangement.
• Pump 420 can include an outlet orifice like that of pump 10, a bypass orifice like that of either pump 10 or pump 330, or both an outlet orifice and bypass orifice.
• the catheter-accumulator combination as shown in Fig. 4 should accomplish the following objectives.
• the accumulator 436 should be compliant enough to receive the entire volume of a single pump stroke with a pressure increase which is low enough so that pump operation is not disturbed. This is not a difficult requirement because the pump plunger is already partly pulled in before a significant back pressure develops in the accumulator 436, and in that position an increased magnetic force is available to the pump plunger.
• the compliance of the accumulator 436 should be low enough so that some moderate back pressure builds up within the accumulator during a pump stroke. This has the effect of allowing the pump 420 to operate more accurately with forward pressure differences by providing a temporary pressure rise across the pump to help decelerate the inertial flow.
• catheter 440 should be large enough so that the volume of a single pump stroke is completely discharged from the accumulator 436 in the interval between pump pulses. Also, the dimensions of catheter 440 and the compliance of accumulator 436 should be such that oscillations of the catheter-accumulator combination are critically damped or overdamped by viscous flow through the catheter 440.
• accumulator 436 should be large enough to receive the volume of a single stroke of pump 420 with a pressure increase no greater than a predetermined maximum amount. Accumulator 436 should be small enough so that the pressure increases by at least a predetermined minimum amount during the stroke of pump 420. Catheter 440 should discharge its contents completely between strokes of pump 420. The combination of catheter 440 and accumulator 436 when considered independent of pump 420 should be critically damped.
• Fig. 5 illustrates a pump according to the present invention which delivers a reduced stroke volume of fluid as compared to the pump of Fig. 1-3 and which has the ability to continue operation with bubbles present in the fluid flow.
• a reduction in the displacement of a pump of the type shown in Figs. 1-3 would be accomplished by reducing either the length of the plunger stroke or the piston diameter. Reducing the length of the plunger stroke would reduce the displacement while leaving unchanged the rest volume of the pump chamber (bounded by the piston face and the two check valves) . This would reduce the pressure head against which a bubble (assumed to fill the volume of the pump chamber) could be pumped, and this reduction can be predicted fairly accurately.
• a solenoid piston pump of the type shown in Figs. 1-3 to continue pumping against a pressure head with bubbles in the fluid stream depends primarily upon the maintenance of a liquid seal between the armature piston and surrounding passage, the pressure drop across the two check valves, and the volume of the bubble captured in the pump chamber relative to the volume of the pump stroke.
• the term pump chamber is intended to include the interior region of the pump housing between the main check valve, the bypass check valve and the piston face.
• the fluid seal is relatively durable so long as the pump is wet. The most important variable is therefore the volume of the trapped bubble. During passage of a large bubble through the pump the entire rest volume of the pump chamber can be expected to be filled with gas.
• the rest volume is the volume of the above-defined pump chamber when the armature is at the rest. Reduction of the bubble volume therefore depends primarily on the rest volume of the pump chamber, and the rest volume in pumps of the type shown in Figs. 1-3 depends strongly upon the design of the main check valve. Therefore, in accordance with the present invention the small displacement pump 450 shown in Fig. 5 has a main check valve configuration which allows a significant reduction in the rest volume of the pump chamber.
• the check valve spring is located external to the pump chamber so that the rest volume of the pump chamber can be significantly reduced. The motivation for the change in the check valve design is in part to achieve a reduction in the rest volume of the pump chamber but it is also necessary in order to overcome the difficulty of making a check valve spring having the required characteristics while fitting into the reduced diameter space.
• the pump 450 of Fig. 5 includes a housing, armature and electromagnet means identical to those of the pumps in Figs. 1-3. Accordingly, components in the pump 450 identical to those in the pumps of Figs. 1-3 are identified by the same reference numerals provided with a double prime designation.
• Inlet 18" is defined by a ferrule element 452 which abuts the axial end face of housing portion 30" and which has a central boss-like extension 454 which fits into a recess provided in the end face of housing portion 30".
• Extension 454 defines an interior chamber 456 which is in fluid communication with the inner passage of housing portion 30" via an axial bore or passage 458.
• Pump 450 includes check valve means 460 comprising a valve element 462 within the inner passage of housing portion 30" and axially adjacent the armature piston portion 250".
• a valve seat element 464 is held between the end of ferrule extension 454 and housing portion 30" and is provided with a central opening 466 which is in registry with passage 458.
• a check valve spring 470 is located within chamber 456 of ferrule 452, one end of spring 470 contacting the inner wall surface of chamber 456 and the other end 474 of spring 470 being connected to valve element 462 by a link or connecting member 476, one end of which is connected to end 474 of spring 470 and the other end of which is secured to a central extension 478 on valve element 462.
• check valve spring 470 is located external to the fluid chambers of pump 450.
• the rest volume resulting from locating the check valve spring 470 in the fluid chamber of pump 450 is thereby eliminated and the space available for spring 470 is large enough so that the desired spring rate is easily achieved.
• the arrangement of Fig. 5 maintains the feature of the basic configuration of the pump of Figs. 1-3 by which the main check valve opens in response to a small pressure difference during the pump stroke but is held closed by a large spring force when at rest.
• Valve seat element 464 is formed from flat sheet rubber and clamped between ferrule extension 454 and housing portion 30" for sealing. To this end extension 454 is provided with an annular extension 484 on the axial end thereof which locally compresses the rubber seat 464 for reliable sealing.
• Valve element 462 is of metal such as titanium and the clearance with the surface of the housing passage can be accurately controlled.
• Element 462 is provided with an annular skirt 490 on the one surface thereof to enhance sealing contact with seat element 464.
• the small displacement pump 450 can be provided with a bypass orifice in a manner similar to either of the pumps 10 or 330 of Figs. 1-3.
• passage 274" can be made small enough in diameter to serve as a bypass orifice in the manner previously described.
• pump 450 can be provided with an orifice in the path of fluid flow from the pump outlet in a manner similar to that of pump 10 in Fig. 1.
• pump 450 can include either or both of bypass or outlet orifices depending upon the requirements of the fluid system of which it is a part.
• Pump 450 operates in a manner similar to pump 10 and 330 in pumping fluid therethrough.
• Fig. 6 shows an alternative version of the pump of Fig. 5 .
• components similar to those of the pump of Fig. 5 are identified by the same reference numeral provided with a prime designation.
• components similar to those of the pump of Figs. 1-3 have the same reference numeral with a triple prime designation.
• the main check valve is similar to that shown in Fig. 5 except that the conical check valve spring 500 is retained in its position between valve element 462 and the piston face.
• the configuration offers no reduction in the rest volume of the pump chamber but it does increase the diameter of the check valve at the diameter at which it seals as compared to the configurations of Figs. 1-3. It is believed that it will improve the dynamics of the flow during the early part of the pump stroke.

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• 1995
  • 1995-03-09 AU AU19913/95A patent/AU1991395A/en not_active Abandoned
  • 1995-03-09 DE DE69535019T patent/DE69535019T2/de not_active Expired - Fee Related
  • 1995-03-09 EP EP95912901A patent/EP0760059B1/de not_active Expired - Lifetime
  • 1995-03-09 WO PCT/US1995/003118 patent/WO1995025223A1/en active IP Right Grant
• 1997
  • 1997-02-24 US US08/804,948 patent/US5797733A/en not_active Expired - Lifetime
• 1998
  • 1998-08-18 US US09/135,760 patent/US5915929A/en not_active Expired - Lifetime
• 1999
  • 1999-05-18 US US09/315,369 patent/US6227818B1/en not_active Expired - Lifetime
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